Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
  • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
  • F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
  • F25D17/06—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
  • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
  • F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
  • F25D17/06—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation
  • F25D17/062—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation in household refrigerators
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
  • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
  • F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
  • F25D17/042—Air treating means within refrigerated spaces
  • F25D17/045—Air flow control arrangements
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
  • F25D2317/00—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
  • F25D2317/06—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation
  • F25D2317/063—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation with air guides
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
  • F25D2317/00—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
  • F25D2317/06—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation
  • F25D2317/068—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the fans
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
  • F25D2317/00—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
  • F25D2317/06—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation
  • F25D2317/068—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the fans
  • F25D2317/0683—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the fans the fans not of the axial type
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
  • F25D2400/00—General features of, or devices for refrigerators, cold rooms, ice-boxes, or for cooling or freezing apparatus not covered by any other subclass
  • F25D2400/28—Quick cooling

Definitions

• the disclosure relates to a blower and a refrigerator.
• a refrigerator has had a storage compartment subdivided to suit objects to be cooled.
• the subdivided storage compartment is arranged in a convenient position for the user to use.
• it has been common to install a ventilation path having a high ventilation resistance and a ventilation path having a low ventilation resistance so as to properly distribute cold air to each storage compartment.
• a blower configured to deliver cold air to two ventilation paths.
• the blower includes a casing having a spiral inner circumferential surface, and an impeller rotatably installed in the casing. Particularly, between the inner circumferential surface of the casing and a blowing surface of the impeller, a first case flow path is provided and at the same time, a second case flow path branched from the first case flow path is provided.
• the blower disclosed in patent document 1 may blow a large amount of high static pressure air from the first case flow path and at the same time blow a small amount of air from the second case flow path.
• the blower may supply cold air to a ventilation path having a high ventilation resistance from the first case flow path and may supply cold air to a ventilation path having a low ventilation resistance from the second case flow path. Therefore, the blower may properly distribute the cold air to each storage compartment.
• the impeller is fixed to the casing through a support member.
• the support member is fixed to the casing through a fixer protruding outward from a blowing surface of the impeller. Therefore, in this structure, the fixer is installed inside the first case flow path. As a result, the flow of cold air in the first case flow path is obstructed by the fixer, and this causes a situation in which the appropriate amount of cold air is not distributed from the first case flow path to the second case flow path.
• blower configure to distribute an appropriate amount of cold air from a first case flow path to a second case flow path.
• a blower configured to circulate cold air inside a body of a refrigerator
• the blower includes a casing, an impeller accommodated in the casing, and a support member configured to support the impeller against the casing.
• the impeller includes a disk-shaped base plate rotatably supported by the support member.
• the casing includes an inner circumferential surface extending so as to gradually move away from an outer circumference of the base plate toward a rotational direction of the impeller at a predetermined position around the outer circumference of the base plate, and a first case flow path between the inner circumferential surface and the outer circumference.
• An introduction port configured to introduce the cold air to a second case flow path branched from the first case flow path is formed on the inner circumferential surface of the casing.
• the support member includes a fixer provided to protrude outward than the outer circumference of the base plate and the support member is fixed to the casing through the fixer.
• An end portion of the fixer which is positioned on the outermost side with respect to the outer circumference of the base plate, is positioned in a non-distribution region that is other than a distribution region between a first reference line connecting a rotating shaft to a rim on a side opposite to the rotational direction of the introduction port, and a second reference line connecting the rotating shaft to a rim on a side in the rotational direction of the introduction port.
• the fixer may have little effect on the cold air flow in the distribution region that most affects an amount of the cold air distributed from the first case flow path to the second case flow path. Therefore, it is possible to distribute an appropriate amount of cold air from the first case flow path to the second case flow path.
• the all fixers may be disposed in the non-distribution region.
• the cold air flow in the distribution region may be not disturbed by the fixer. Accordingly, it is possible to distribute more appropriate amount of cold air from the first case flow path to the second case flow path.
• the introduction port as a specific configuration of the blower may be formed in a region between a third reference line connecting the rotating shaft to the predetermined position and a fourth reference line generated by rotating the third reference line toward the rotational direction by 45 ° with respect to the rotating shaft.
• a distance between the inner circumferential surface and the blowing surface on the third reference line may be 2 mm or more and 15 mm or less, and an angle between a vertical line of the first reference line and a tangent of the rim of the second case flow path may be greater than 0 ° and less than 60 °
• a refrigerator includes a blower, a first cold air flow path configured to communicate with a first case flow path of the blower, and a second cold air flow path configured to communicate with a second case flow path of the blower.
• the blower may supply an appropriate amount of cold air, which is appropriate for each ventilation path, even when ventilation paths configured to guide the cold air to the each storage compartment has different ventilation resistance.
• the refrigerator may further include a body in which the first cold air flow path and the second cold air flow path are provided.
• the blower may be removably installed in the body of the refrigerator.
• the refrigerator may further include a cooling unit configured to cool the cold air to be supplied to an intake port of the blower and the cooling unit may be removably installed in the body of the refrigerator.
• the maintenance may be improved because the blower and the cooling unit are removable from the body of the refrigerator.
• a discharge amount per unit time discharged from the outlet hole of the second cold air flow path to the inside of the body may be 20% or less of a total discharge amount per unit time discharged from the outlet hole of the first cold air flow path and the second cold air flow path to the inside of the body.
• the ratio of the air amount As mentioned above, the amount of the cold air discharged from the first case flow path to the second case flow path may be minimized, and thus the air amount and static pressure of the first case flow path may be increased.
• the outlet hole of the first cold air flow path and the outlet hole of the second cold air flow path may be arranged in such a way that one thereof is arranged on one side with respect to the rotating shaft, and the other thereof is arranged on a side opposite to the one side with respect to the rotating shaft.
• an outlet hole disposed farthest from the rotating shaft may be apart from the rotating shaft 500 mm or more.
• first cold air flow path may extend upward in the inside of the body.
• the cold air supplied to the upper portion of the inside of the body may flow downward so as to efficiently cool the inside of the body, thereby saving energy in the refrigerator.
• the refrigerator may further include a first storage compartment to which cold air is supplied from the outlet hole of the first cold air flow path, and a second storage compartment to which cold air is supplied from the outlet hole of the second cold air flow path.
• a volume of the second storage compartment may be less than a volume of the first storage compartment.
• an outlet hole disposed farthest from the rotating shaft may be apart from the rotating shaft 500 mm or more.
• the second storage compartment may be used as an ice making compartment having a relatively small volume and the first storage compartment may be used as a freezing compartment having a relatively large volume, and thus it is possible to supply an appropriate amount of cold air for each storage compartment.
• FIG. 1 is a cross-sectional view schematically illustrating an internal structure of the refrigerator according to an embodiment of the disclosure
• FIG. 2 is an enlarged sectional view schematically illustrating a part of the internal structure of the refrigerator according to an embodiment of the disclosure
• FIG. 3 is a perspective view schematically illustrating a blower of the refrigerator according to an embodiment of the disclosure
• FIG. 4 is a center cross-sectional view schematically illustrating an impeller and a support member of the blower of the refrigerator according to an embodiment of the disclosure
• FIG. 5 is a front view schematically illustrating the blower of the refrigerator according to an embodiment of the disclosure.
• FIG. 6 is a front view schematically illustrating the blower of the refrigerator according to the embodiment of the disclosure.
• FIGS. 1 through 6, discussed below, and the various embodiments used to describe the principles of the present disclosure in this patent document are by way of illustration only and should not be construed in any way to limit the scope of the disclosure. Those skilled in the art will understand that the principles of the present disclosure may be implemented in any suitably arranged system or device.
• a refrigerator according to the disclosure is mainly used in homes.
• the disclosure is not limited to a household refrigerator, and may be applied to a commercial refrigerator.
• the refrigerator according to the disclosure includes not only a refrigerator including a refrigerating compartment and a freezing compartment, but also a refrigerator including only a refrigerating compartment, or a refrigerator including only a freezing compartment.
• a refrigerator 100 includes a refrigerator body 10 and a cooling unit 20 connected to the refrigerator body 10, as shown in FIG. 1.
• the cooling unit 20 according to an embodiment is configured to be removably connected to the refrigerator body 10 from a bottom side (with respect to FIG. 1, a lower side) or a back side (with respect to FIG. 1, a right side).
• the cooling unit 20 is configured in such a way that each device constituting a refrigeration cycle device is installed in a unit body 21 forming an outer wall 100a of the refrigerator 100 together with the refrigerator body 10.
• Each of the devices includes a compressor (not shown), a condenser (not shown), and an evaporator 22.
• the compressor and the condenser are installed to be disposed on the outside of the body of the refrigerator 100 in a state in which the cooling unit 20 is connected to the refrigerator body 10.
• the evaporator 22 is installed in the unit body 21 to be disposed inside the body of the refrigerator 100 in a state in which the cooling unit 20 is connected to the refrigerator body 10.
• the refrigerator body 10 is formed in a case shape including a door 11 configured to open the case toward the front (with respect to FIG. 1, a left side).
• the inside of the refrigerator body 10 is divided into a front side (front surface side) and a rear side (rear surface side) by a partition member 12 when viewed from the door 11 side. Accordingly, in the inside of the refrigerator body 10, a cooling room CR is formed in front of the partition member 12, and a circulation path L is formed behind the partition member 12.
• the cooling room CR is a space in which food to be cooled is placed. Accordingly, the cooling room CR may be regarded as a storage compartment. Further, the cooling room CR may be divided into a plurality of cooling spaces cr arranged vertically by shelves.
• the circulation path L is a passage for cooling and circulating the cold air inside the body. The circulation path L is formed to vertically extend inside the body. Further, the circulation path L is configured to cool the cold air taken from the cooling room CR, and then discharge the cooled air to each cooling space cr of the cooling room CR.
• the circulation path L is configured to suction cold air from an inlet hole H, which is formed in the partition member 12 to communicate with the lowest cooling space cr, and then discharge the cold air to an outlet hole h, which is formed in the partition member 12 to communicate with each cooling space cr.
• the evaporator 22 of the cooling unit 20 configured to cool the cold air, which is suctioned from the inlet hole H
• a blower 30 configured to blow the cold air are arranged from an upstream side to a downstream side.
• the circulation path L includes a first cold air flow path L1 and a second cold air flow path L2 constituting the downstream side than the blower 30.
• the first cold air flow path L1 guides the cold air sent from the blower 30 upward than the blower 30 and the first cold air flow path L1 is formed in a duct shape.
• the second cold air flow path L2 guides the cold air sent from the blower 30 downward than the blower 30 and the second cold air flow path L2 is formed in a duct shape.
• the first cold air flow path L1 includes an outlet hole h, which is configured to communicate with a plurality of cooling space cr positioned in the upper portion of the cooling room CR, among the outlet holes h. Therefore, the first cold air flow path L1 is configured to supply cold air, which is sent from the blower 30, to each of the cooling spaces cr located in the upper portion of the inside of the body.
• the first cooling air flow path L1 according to an embodiment is configured to guide the cold air to other cooling spaces cr except the lowest cooling space cr.
• an outlet hole h farthest from the blower 30 is arranged at a position far from a rotation axis X of the impeller 50, which is provided in the blower 30, by 500mm or more.
• the outlet hole h is set to be placed a position far from the rotation axis X of the impeller 50 by 500mm or more along the first cold air flow path L1.
• the second cold air flow path L2 includes an outlet hole h, which is configured to communicate with at least one cooling space cr positioned in the lower portion of the cooling room CR, among the outlet holes h. Therefore, the second cold air flow path L2 is configured to supply cold air, which is sent from the blower 30, to the at least cooling spaces cr located in the lower portion of the inside of the body.
• the second cooling air flow path L2 according to an embodiment is configured to guide the cold air to the lowest cooling spaces cr.
• a length of the first cold air flow path L1 is greater than a length of the second cold air flow path L2.
• the first cold air flow path L1 is configured to have greater ventilation resistance than that of the second cold air flow path L2.
• a total volume of the cooling space cr, to which cold air is supplied from the first cold air flow path L1 is greater than a total volume of the cooling space cr, to which cold air is supplied from the second cold air flow path L2.
• the evaporator 22 corresponds to a heat exchanger, and is configured to pass cold air through a plurality of fins.
• the evaporator 22 is arranged between the inlet hole H of the circulation path L and the blower 30. Accordingly, cold air, which is taken into the circulation path L from the inlet hole H, is cooled while passing through the evaporator 22.
• the blower 30 is provided on the partition member 12. Particularly, with respect to the partition member 12, the blower 30 is installed at a distance from the inner wall 10a on the rear side of the refrigerator body 10. In addition, the blower 30 includes an intake port 31 on a surface facing the inner wall 10a. Therefore, the blower 30 is configured to distribute the cold air sucked from the intake port 31 into the first cold air flow path L1 and the second cold air flow path L2.
• the partition member 12 has a structure that is divided up and down, and the partition member 12 in the lower side is removable from the refrigerator body 10.
• the blower 30 is provided on the lower partition member 12.
• the blower 30 includes a casing 40 including the intake port 31, the impeller 50 accommodated in the casing 40, and a support member 60 configured to support the impeller 50 against the casing 40.
• the casing 40 accommodates the impeller 50.
• the casing 40 incudes a casing body 41 opened in one direction and a cover 42 configured to close the opening of the casing body 41, as shown in FIG. 3.
• the cover 42 includes a through hole 42a forming the intake port 31.
• the cover 42 according to an embodiment is configured to be fixed to the partition member 12 by means such as screwing. Further, the casing body 41 is sandwiched between the cover 42 and the partition member 12 and thus the casing body 41 is integral with the partition member 12.
• the casing body 41 includes an end surface S1a facing the intake port 31 and an inner circumferential surface S1b standing on an outer edge (circumference) of the end surface S1a. At least a portion of the inner circumferential surface S1b of the casing body 41 is formed in a spiral (swirl shape).
• the impeller 50 is installed on the end surface S1a of the casing body 41 through the support member 60.
• the impeller 50 is a centrifugal fan. Particularly, as shown in FIG. 4, the impeller 50 includes a disc-shaped base plate 51 and a plurality of blades 52 protruding from the base plate 51in the direction of the rotation axis X.
• the plurality of blades 52 is disposed at a distance from each other around the rotation axis X, and extends outwardly (that is, an outside of a diameter direction of the base plate 51) from the rotation axis X.
• Each blade 52 extends from the rotation axis X to pass an axial line extending in the diameter direction of the base plate 51.
• one end of the blade in a rotational direction with respect to the corresponding the axial line is placed in the rotation axis X side (that is, an inside of the diameter direction of the base plate 51) and the other end of the blade in a direction opposite to the rotational direction with respect to the corresponding the axial line reaches an outer circumference 51e of the base plate 51.
• the impeller 50 includes a blowing surface S2 formed by the outer edge of the plurality of blades 52.
• the blowing surface S2 has a circular shape when viewed from the rotation axis X direction, and has a concentric circular shape with the outer circumference 51e of the base plate 51.
• the impeller 50 according to an embodiment includes a reinforcing frame 53 extending along the blowing surface S2, and connected to each blade 52 (refer to FIG. 4).
• the support member 60 supports the impeller 50 against the end surface S1a of the casing body 41, as shown in FIG. 4.
• the support member 60 includes a support plate 61 configured to support a rotation mechanism 70 such as a motor, and a plurality of fixers 62 protruding from an outer edge of the support plate 61.
• the support plate 61 according to an embodiment includes a structure to hold the rotation mechanism 70 at the center, and the impeller 50 is fixed to a shaft center 71 protruding from the rotation mechanism 70 and serving as the rotation axis X. In this state, each fixer 62 protrudes more outward than the outer circumference 51e of the base plate 51 constituting the impeller 50.
• a portion of the support member 60 except for the fixer 62 of the support plate 61 is formed in a circular shape having a diameter greater than the base plate 51.
• the impeller 50 is installed in such a way that, from a predetermined P1, the outer circumference 51e of the base plate 51 faces to gradually move away from a spiral inner circumferential surface S1b of the casing body 41 in a rotational direction. That is, at the predetermined position P1, the outer circumference 51e of the base plate 51 is installed closest to the inner circumferential surface S1b.
• the impeller 50 is installed in such a way that a part of the outer circumference 51e of the base plate 51, which is in the rotational direction side and placed in at a position P2 (hereinafter referred to as the closest position P2), which is the closest to the certain position P1 of the inner circumferential surface S1b, gradually moves away from the inner circumferential surface S1b. Accordingly, in the casing main body 41, a first case flow path L3 which gradually expands toward the rotational direction of the impeller 50 is formed between the inner circumferential surface S1b and the outer circumference 51e.
• the inner circumferential surface S1b and the blowing surface S2 are set such that a width W between the positions closest to each other (between the predetermined position P1 and the closest position P2) is 2 mm or more and 15 mm or less.
• the casing body 41 includes a second case flow path l2 branched from the first case flow path L3.
• a first discharge port 32 configured to discharge cold air from the first case flow path L3 to the outside of the casing body 41 is formed at a surface at a position opposite to the rotational direction of the impeller 50 at the predetermined position P1, that is, a surface positioned on the downstream of the first case flow path L3.
• the first case flow path L3 is in a state in communication with the first cold air flow path L1 through the first discharge port 32.
• an introduction port 33 configured to introduce a part of the cold air flowing through the first case flow path L3 into the second case flow path l2 is formed on the inner circumferential surface S1b of the casing main body 41.
• the introduction port 33 is formed on a surface positioned on the side in the rotational direction from the predetermined position P1, that is, on the surface positioned on the upstream side of the first case flow path L3.
• a line connecting the rotation axis X to a rim 33a on a side opposite to the rotational direction of the introduction port 33 is a first reference line ⁇
• a line connecting the rotation axis X to a rim 33b on a side in the rotational direction of the introduction port 33 is a second reference line ⁇ .
• a region between the first reference line ⁇ and the second reference line ⁇ in the first case flow path L3 is a distribution region R1
• a region except for the distribution region R1 is a non-distribution region R2.
• the support member 60 is arranged in such a way that an end portion 61a of the fixer 62, which is positioned on the outermost side with respect to the outer circumference 51e of the base plate 51, is positioned in the non-distribution region R2.
• fixer 62 when the end portion 61a is disposed in the non-distribution region R2, a part of the fixer 62 may be arranged in the distribution region R1. However, it is appropriate that all the end portions 61a are arranged in the non-distribution region R2 as in the fixer 62 according to an embodiment.
• a line connecting the rotation axis X to the predetermined position P1 of the inner circumferential surface S1b (or the closest position P2 of the blowing surface S2) is a third reference line ⁇
• a line generated by rotating the third reference line ⁇ toward the rotational direction of the impeller 50 by 45 ° with respect to the rotation axis X is a fourth reference line ⁇ . Therefore, the introduction port 33 is formed in a region between the third reference line ⁇ and the fourth reference line ⁇ .
• the introduction port 33 according to an embodiment is formed in such a way that the first reference line ⁇ coincides with the third reference line ⁇ and the second reference line ⁇ coincides with the fourth reference line ⁇ .
• the second case flow path l2 extends in a state in which the rim 33a of the introduction port 33 on the third reference line ⁇ side functions as a start point SP of the ventilation path (in this embodiment, the same position as the predetermined position P1).
• the second case flow path l2 extends substantially in parallel with the first case flow path L3.
• a second discharge port 34 configured to discharge cold air from the second case flow path l2 is formed on the downstream side of the second case flow path l2.
• the second case flow path l2 is in a state in communication with the second cold air flow path L2 through the second discharge port 34.
• an inner surface S4 extending from the starting point SP of the second case flow path l2 is set to allow an angle ⁇ formed by a tangent t at the starting point SP and a vertical line p of the first reference line ⁇ to be greater than 0 ° and less than 60 °.
• the angle ⁇ represents an angle generated by spreading the tangent t with respect to the vertical line p outward about the starting point SP.
• the cold air which flows into the circulation path L from the lowest cooling space cr through the inlet hole H, is cooled while passing through the evaporator 22. Subsequently, the cold air cooled by passing through the evaporator 22 is sucked into the casing body 41 of the blower 30 through the intake port 31. The cold air sucked into the casing body 41 is introduced into the first case flow path L3 by centrifugal force according to the rotation of the impeller 50, and at the same time, a part of the cold air introduced into the first case flow path L3 is introduced into the second case flow path l2.
• cold air which is not introduced into the second case flow path l2 but passes through the first case flow path L3, is introduced into the first cold air flow path L1 through the first discharge port 32.
• the cold air introduced into the second case flow path l2 is introduced into the second cold air flow path L2 through the second discharge port 34.
• the cold air introduced into the first cold air flow path L1 is supplied to the cooling space cr above the blower 30 through the outlet hole h.
• the cold air introduced into the second cold air flow path L2 is supplied to the cooling space cr below the blower 30 through the outlet hole h.
• the cooling room CR includes one space divided by shelves, but the cooling room CR may include two spaces.
• the cooling room CR may be divided into a large-volume refrigerating compartment and a small-volume ice-making compartment.
• the blower 30 may be configured to supply cold air discharged from the first case flow path L3 to the large-volume refrigerating compartment, and to supply cold air discharged from the second case flow path l2 to the small volume ice-making compartment.
• the casing 40 may be formed in such a way that an amount of cold air per unit time supplied to the storage compartment through the second case flow path l2 is 20% or less of an amount of cold air per unit time supplied to the storage compartment through the first case flow path L3 and the second case flow path l2.
• the blower 30 is configured to supply cold air to the cooling space cr above the blower 30 through the first case flow path L3, and configured to supply cold air to the cooling space cr below the blower 30 through the second case flow path l2, but is not limited thereto. Therefore, the blower 30 may be configured to supply cold air to the cooling space cr above the blower 30 through both the first case flow path L3 and the second case flow path l2.
• the casing 40 according to the above embodiment is provided with the second case flow path l2 extending to follow the spiral inner circumferential surface S1b in the casing body 41, but the second case flow path l2 may not follow the spiral inner circumferential surface S1b.
• the introduction port 33 may be provided in such a way that the rim 33a, through which the first reference line ⁇ passes, is positioned on the fourth reference line ⁇ side other than the third reference line ⁇ .
• the introduction port 33 may be provided in such a way that the rim 33b, through which the second reference line ⁇ passes, is positioned on the third reference line ⁇ side other than the fourth reference line ⁇ . That is, the introduction port 33 may be formed in a region between the third reference line ⁇ and the fourth reference line ⁇ .
• the entire inner circumferential surface S1b of the casing body 41 is formed in a spiral shape, but is not limited thereto.
• a part of the inner circumferential surface S1b of the casing main body 41, which is positioned at a side in the rotational direction of the impeller 50 from the predetermined position P1, may be formed in a spiral shape.
• the fixer 62 of the support member 60 is fixed in a state of protruding from the end surface S1a of the casing body 41.
• a groove in which the support member 60 is accommodated may be formed on the end surface S1a of the casing main body 41, and the support member 60 may be fitted into the groove. In this case, because the fixer 62 is accommodated in the groove, the fixer 62 may not protrude from the end surface S1a.
• blower 30 may employ a turbo fan.

Landscapes

• Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Physics & Mathematics (AREA)
• Mechanical Engineering (AREA)
• Thermal Sciences (AREA)
• General Engineering & Computer Science (AREA)
• Cold Air Circulating Systems And Constructional Details In Refrigerators (AREA)

Applications Claiming Priority (3)

Publications (2)

Family

ID=73651493

Family Applications (1)

Country Status (3)

Families Citing this family (5)

Family Cites Families (16)

• 2020
  • 2020-06-04 EP EP20818881.3A patent/EP3963272A4/de active Pending
  • 2020-06-04 WO PCT/KR2020/007296 patent/WO2020246829A1/en not_active Ceased
  • 2020-06-05 US US16/894,704 patent/US11933533B2/en active Active

Also Published As

Similar Documents

Legal Events